DE19900428A1 - Rolling mill for rolling rod-shaped rolling stock, e.g. B. steel bars or wire - Google Patents

Abstract

Rolling mill for rolling rod-shaped rolling stock (11), e.g. B. bar steel or wire, DOLLAR A - with several adjustable via hydraulic cylinder units (12) on roll gaps (s3-s10), from the rolling stock (11) one after the other, combined into rolling stand pairs active rolling stands (3-10), by means of which the rolling stock ( 11) with the application of rolling forces (F3-F10) to an end height (h) and a perpendicular end width (b), DOLLAR A - whereby the hydraulic cylinder units (12) can be controlled by roll gap controls (13), by means of which the spring force-dependent spring-ups active roll stands (3-10) can be compensated for at least in fractions (t3-t10), and DOLLAR A - whereby the fractions (t3-t10) can be set separately for each active roll stand (3-10).

Description

The present invention relates to a rolling mill for rolling rod-shaped Rolled material, e.g. B. steel bars or wire, with several adjustable on nips, from the rolling stock passed through one after the other to form pairs of rolling stands active rolling stands, by means of which the rolling stock with the application of Rolling forces can be rolled to a final height and a vertical width perpendicular thereto.

Rolling mills of this type are generally known. The individual mill stands one Such rolling mill are alternately as horizontal and as vertical stands trained, the last pass rolling mill always the end profile, z. B. a round, square or hexagonal caliber.

In the prior art, the roll stands are open by means of electric or hydraulic motors Roll gap adjustable. The setting of the roll gap can usually only in load-free state. It is not possible to adjust the nips under load possible. It is only possible to change the speeds of the roll stands during the Operating change. Other interventions such as B. are a roll gap correction not possible.

In the older, unpublished German patent application 198 31 481.7 is a rolling mill for rolling rod-shaped rolling stock is described, the meh rere adjustable on roll gap via hydraulic cylinder units of the rolling stock has successively passed through rolling stands, by means of which the roll  well with the application of rolling forces to a final height and a lower one right end width is rollable, the hydraulic cylinder units from Walz gap controls can be controlled, by means of which spring-force-related suspensions of the active roll stands can be compensated for at least to a fraction.

The task is based on the prior art mentioned at the beginning of the present invention therein, a rolling mill for rolling rod-shaped To create rolling stock in which the roll gaps are adjustable under load and are also adapt the rolling behavior of the roll stands to the respective rolling stock is cash.

The task is solved by

• - That the roll gaps of the active roll stands via hydraulic cylinder units are adjustable,
• - That the hydraulic cylinder units can be controlled by roll gap controls are, by means of which spring force-dependent spring-ups of the active roll stands are at least partially compensable, and
• - That the fractions can be set separately for each active roll stand.

Due to the use of hydraulic cylinder units as adjustment devices an adjustment of the roll gap under load is possible for the roll gap. Because of The compensatability of the spring forces caused by the rolling force occurs automatically table correction of these suspensions. Since in this case a possible roll mistake However, if the full extent were rolled in width, the springing will only close compensated for a fraction. Due to the adjustability of the fractions, the Optimally adapt rolling stands to their respective task within the rolling mill bar.  

The rolling stands take over in the rolling train depending on the rolling Product, various tasks, namely either an acceptance or a so-called called presizing or a so-called sizing.

The main task of acceptance stands is to make the cross section of the rolling stock possible as much as possible. For this purpose, the respective roll stand should be as rigid as possible his. In connection with a monitor control even with this roller the cross-section can be optimized.

The main task of presizing scaffolds is the ratio of height to width of the rolling stock in front of the subsequent sizing stands to a defined value adjust. For this, z. B. with a round end profile, the oval frameworks high and the round frameworks have an optimal rigidity. Because by that temperature and cross-sectional disturbances are even on both dimensions distributed.

The main task of sizing stands is to roll the rolling stock to the desired end dimensions and at the same time to ensure good ovality of the rolling stock. For this, z. B. with a round end profile, the oval frame has a relatively high and the round frame a lower, optimal rigidity. The following settings are optimal:

• - The spring force-related suspension of the pass through later by the rolling stock Sizing scaffolding is compensated to a smaller fraction than that Spring force-related spring-back of that previously passed through by the rolling stock Sizing frame.
• - The spring force-related suspension of the pass through later by the rolling stock A smaller fraction of the presizing framework is compensated for than that Spring force-related spring-back of that previously passed through by the rolling stock Presizing framework.  
• - The spring force-related spring-ups of the take-off stands become at least least essentially fully compensated.

The last two active roll stands always work in sizing mode. At least a pair of mill stands directly upstream of the sizing stands works in Presizing mode. The remaining mill stands work in acceptance mode. Because of The adjustability of the fractions can now be set which rolling stands work in sizing mode, in presizing mode and in acceptance mode.

The ovality of the end product is particularly good if the rolling force-related Springing of the sizing frames was compensated on average for smaller fractions are called the spring force-related spring-ups of the presizing stands.

The tolerance compliance is even better when the rolling stock from the presizingge equip is rolled in such a way that the sizing stands in their most favorable dynamic operated richly. This can e.g. B. can be achieved in that the roller column of the presizing stands is determined from the rolling gaps of the sizing stands the.

The dimensional accuracy of the rolled rolling stock can be increased even further, if a measuring device is added to the sizing stand that is later passed through by the rolling stock device for recording the final height and final width of the rolling stock and the roll gaps of the sizing stands based on the recorded end height and end wide can be corrected (monitor control).

The rolling stock can be rolled even more precisely, even if the other rolling mill pairs of stands, preferably even any other rolling stand, measuring devices are subordinate to record the height and width of the rolling stock. In this In this case, the roll gaps for these roll stands can be taken directly from the detected heights and widths can be determined.  

Between the individual roll stands, the one usually occurs in the rolling stock tend train detected and the speeds of the rolling stands adjusted so that the train is constant. In addition, it is possible with the measuring devices Cross-section of the rolling stock between the roll stands. The train- and / or height and width measurements can be used Optimize fractions during rolling.

When a new rolling stock is rolled, the first billet should already be possible have the correct final dimensions in a batch. He can do this be enough that the rolling mill ei a storage device for storing a variety of material properties of rolled goods, the final height, the final width, the framework parameters and the framework settings, an input device for entering the material properties, the final height and the final width of a new rolling stock to be rolled and a comparison device for comparing the dimensions material properties, the final height and the final width of the roll to be rolled guts with the material properties, the final height and the final width of the spit stored rolling stock and the current stand parameters with the saved has th stand parameters, so that the rolling stands with matching Stand parameters when rolling a new rolling stock onto the stand setting conditions for an already rolled rolling stock with corresponding material properties shafts and final dimensions can be preset.

The stand parameters particularly include the roll diameters. The scaffold Settings include in particular the roll gap, the roll speeds and the fractions. The material properties of the rolling stock include in particular the temperature, the initial dimensions and the quality of the rolling stock.

With such presets, when the new stick is actually the one given material properties, an immediate optimal rolling this Bludgeon possible.  

If in the storage device there is also a large number of rolls being rolled rolling parameters resulting from the goods can be stored and the rolling mill is a ver same device for comparing yourself when rolling the new rolling stock resulting rolling parameters with the correct with the new stand settings sponding rolling parameters and an output device for outputting egg Warning signal if there are significant deviations when rolling the new one Rolling stock resulting from the rolling parameters with the new scaffolding lungs corresponding rolling parameters, it is possible to the billet to check whether it actually owns the entered material features.

The rolling parameters include in particular the rolling forces and / or the rolling moments.

Further advantages and details result from the following description exercise of an embodiment. Show in principle

Fig. 1 is a rolling mill for rod-shaped rolling stock and

Fig. 2 shows a hydraulic cylinder unit with a roll gap control.

According to FIG. 1, a rolling mill has rolling stands 1-10 , through which a rolling stock 11 passes in succession. The rolling stock 11 is a rod-shaped rolling stock 11 , for. B. steel bars or wire. The rolling stand 10 is passed through first, the rolling stand 1 as the last. The rolling stands 1 -10 are alternately formed as a horizontal and a vertical stands. You assign z. B. alternately round and oval calibers. The last passed through the rolling stock 11 rolling mill 1 z. B. a round caliber. Two consecutive roll stands 1-10 are combined to form a pair of roll stands.

By means of the rolling stands 1-10 , the rolling stock 11 can be rolled to an end height h and a perpendicular end width b by applying rolling forces F3-F10. The last two roll stands 1 and 2 are inactive according to the example. So you do not roll the rolling stock 11 . The rolling stock 11 only passes through the last two rolling stands 1 , 2 . So only the mill stands 3-10 are active. This is possible because the final dimensions h, b are relatively large according to the exemplary embodiment. With smaller values for the final dimensions h, b, the two last rolling stands 1 , 2 would also be activated.

If the rolling mill is equipped with rolling stands 1-10 , which have quick-change devices, inactive rolling stands - in this case, the rolling stands 1 and 2 - are extended from the rolling mill and retracted into the rolling mill only when required.

The roll stands 1-10 are all constructed the same way. The structure of the roll stand 3 is therefore only described below.

According to FIG. 2, the roll stand 3 is associated with a hydraulic cylinder unit 12, by means of which a roll nip s3 is adjustable under load. The required rolling force F3 is determined by the hydraulic cylinder unit 12 and the working pressure p3 with which it is applied. The hydraulic cylinder unit 12 is controlled by a roll gap control 13 .

Before the start of rolling, the hydraulic cylinder unit 12 is first controlled by the roll gap control 13 in such a way that the roll gap s3 is closed. The working pressure p3 is practically zero. When the roll gap s3 is completely closed, the working pressure p3 increases. Due to the increasing working pressure p3, the force F3 exerted on the roll stand 3 increases. The roll stand 3 thus springs open. The roll gap control 13 is continuously informed of the adjustment pressure a3 of the hydraulic cylinder unit 12 at which working pressure p3. The roll gap control 13 can then determine the zero point of the roll gap s3 and the spring constant C3 of the roll stand 3 from this measurement curve. The spring constant C3 is required in order to determine the spring force-related spring deflection, which results as a product of the spring constant C3 and the rolling force F3.

At the start of rolling, the roll gap control 13 is given a nominal roll gap s3 ^* and an expected rolling force F3 ^* . Due to the known zero point of the roll gap s3 and the known spring constant C3, the Walzspaltrege treatment 13 can then set the hydraulic cylinder unit 12 such that the roll stand 3 assumes the desired roll gap s3 ^* after springing.

Due to various influences, e.g. B. roll eccentricities, cross-section fluctuations of the rolling stock 11 , temperature fluctuations of the rolling stock 11 , etc., the rolling force F3 varies during rolling. As a result, the rolling stand 3 springs more or less in accordance with the variable rolling force F3. Due to the known spring-back behavior of the roll stand 3 , the spring force-related spring-back C3 (F3-F3 ^* ) can be compensated continuously by detecting the working pressure p3 and correspondingly correcting the adjustment travel a3. In the case of the rod-shaped rolling stock 11 , however, this would mean that the height h of the rolling stock 11 emerging from the rolling stand 3 would be correct, but the entire rolling defect would be rolled into the width b. The spring force-related spring-back of the roll stand 3 is therefore preferably only compensated for by a fraction t3. The fraction t3 is the roll gap control 13 by a superordinate computer 14 - see Fig. 1 - specified.

The statements made above regarding the roll stand 3 also apply accordingly to the other active roll stands 4-10 . In particular, the other active roll stands 4-10 are also given a nominal roll gap s4 ^* -s10 ^* , an expected rolling force F4 ^* - F10 ^* and a respective fraction t4-t10.

The sizing stands 3 , 4 only work with optimal dynamics if the cross section of the rolling stock 11 fed to them lies in a predetermined cross-sectional area. Therefore, the rolling stock 11 is always rolled by the rolling stands 5 , 6 , which are directly upstream of the Si zing stands 3 , 4 , in such a way that the sizing stands 3 , 4 are operated in their most favorable dynamic range. The roll stands 5, 6 thus operate as so-called Presizinggerüste 5, 6th

The presizing stands 5 , 6 are further rolling stands 7-10 immediately net. In these, the rolling stock 11 is rolled as much as possible in order to be able to roll it to its final dimensions h, b with a minimum total number of passes. The roll stands 7-10 thus work as so-called acceptance stands 7- 10.

According to embodiment, only the rolling stands 5, 6 as Presizinggerüste 5, 6 are operated. In principle, however, the roll stands could also be operated by two or even three pairs of roll stands as presizing stands.

The fractions t3-t10, to which the spring force-related suspensions of the roll stands 3-10 are compensated, can be set separately. In practice, the following settings have proven to be particularly advantageous:

• - The spring force-related spring-up of the sizing stand 3 is compensated for by a small ren fraction t3 than the spring-force-dependent spring-up of the Si zing stand 4 .
• - The spring force-related spring-back of the presizing stand 5 is compensated for by a smaller fraction t5 than the spring-force-dependent spring-up of the presizing stand 6 .
• - The spring force-related spring-ups of the sizing stands 3 , 4 are compensated on average to smaller fractions t3, t4 than the spring-force-dependent spring-ups of the presizing stands 5 , 6 .
• - The spring force-related spring-ups of the tapping frames 7-10 are 90% -100%, that is, at least essentially in full, compensated.

This compensation of the spring forces caused by the rolling force alone results in a considerable increase in the quality of the rolling stock 11 . In addition, according to FIG. 1, the two inactive roll stands 1 and 2 are followed by a measuring device 15 for detecting the final height h and final width b of the rolling stock 11 . The detected end values h, b are transmitted to the higher-level computer 14 . This continuously calculates new target roll gaps s3 ^* , s4 ^* for the sizing stands 3 , 4 . The roll gaps s3, s4 can thus be corrected on the basis of the detected end height h and the detected end width b.

The superordinate computer 14 can determine the dimensions of the rolling stock 11 between the roll stands 4 and 5 on the basis of the transmitted final dimensions h, b and the desired roll gaps s3 ^* , s4 ^{* of} the sizing stands 3 , 4 . On the basis of these determinable dimensions, the superordinate computer 14 can then also determine target roll gaps s5 ^* , s6 ^* for the presizing stands 5 , 6 and specify their roll gap controls.

Alternatively, it is also possible, in addition to the measuring device 15 , to provide 1 further measuring devices 16-19 behind the roll stand, which are arranged directly behind the pair of sizing rolls, the pair of presizing rolls and the take-off roll pairs. Preferably even arranged behind each rolling stand 1 -10 measuring means 15-19. By means of the superordinate computer 14 , the respective roll gap regulations of the individual roll stands 3 -10 can then be predefined directly, which roll gap s3 ^* -s10 ^* they should set.

Tension measuring devices are arranged between the roll stands 1-10 . For the sake of clarity, only one of the tension measuring devices, namely the tension measuring device 20 , is shown in FIG. 1. The measured values of the tension measuring devices 20 are also transmitted to the higher-level computer 14 . By comparing the tensile measurements with the positions of the respective rolling stand 1-10 in advance, the latter can determine whether the fraction t3-t10 by which the roll-related spring-back forces are compensated is optimally set. If necessary, the respective fraction t3-t10 can be corrected, which means that the result can be optimized during rolling.

This correction is even easier if the other measuring devices 16-19 are available. Then it can be concluded directly from the measured heights and widths of the rolling stock 11 behind the roll stands 9 , 7 , 5 and 3 on the optimal fractions t3-t10.

For each rolled material 11 that has already been rolled, a data record is stored in a storage device 21 of the higher-level computer 14 . On the one hand, the data set includes the roll diameters of the roll stands 1-10 as stand parameters, on the other hand the stand settings s3-s10, t3-t10 of the roll stands 1-10 and thirdly the material properties of the rolling stock 11 . For each roll stand 1-10, the roll diameters, the roll gaps s3-s10, the roll speeds and the fractions t3-t10 are stored in particular. Furthermore, it is stored which temperature, which initial dimensions and what quality a rolled rolling stock 11 has. The data record also includes the end height h to be rolled and the end width b to be rolled per rolling stock 11 . Finally, the data set also includes the rolling parameters F3-F10 resulting from the rolling of the rolling stock 11 , that is to say the rolling forces F3-F10 and / or the rolling moments.

The temperature of the rolling stock 11 can be determined, for example, by means of a temperature measuring device 22 which is arranged at the entrance to the rolling train. The material properties of the rolling stock 11 can be entered into the higher-level computer 14 , for example, via a keyboard 23 serving as an input device.

A large number of such data sets (one data set per rolling stock 11 ) can be stored in the storage device 21 . If a new rolling stock 11 is now to be rolled, the material properties of the rolling stock 11 and the final dimensions h, b to be rolled are input into the higher-level computer 14 . The higher-level computer 14 then compares the entered data of the rolling stock 11 to be newly rolled with the stored data records. If he finds a data set whose material properties and final dimensions h, b match those of the rolling stock 11 to be newly rolled, he compares the current stand parameters with the stored stand parameters. If these also match, then he calls the settings s3-s10, t3-t10 corresponding to this from the storage device 21 and outputs them to the roll gap controls 13 of the roll stands 1-10 . This makes it possible to immediately roll the first billet of a new batch to the desired final dimensions h, b with good tolerances. A slow approach to the correct settings s3-Sb, t3-t10 is not necessary.

In addition, the higher-level computer 14 when the new rolling stock 11 is rolled is of course also transmitted the rolling parameters F3-F10 of the roll stands 1-10 which result from the rolling of the new rolling stock 11 . Among other things, the applied rolling forces F3-F10 are transmitted to the higher-level computer 14 . The superordinate computer 14 compares these values with the rolling forces F3-F10 previously stored for an equivalent rolling stock 11 . If during this comparison significant differences, this is an indication that the new rolling 11 but does not match the previously selected rolling well. 11 In this case, an output device 24 , for. B. a monitor 24 , a warning signal. On the basis of this warning signal, an operator can then make appropriate corrections to the settings of the roll stands 1-10 and, if necessary, also arrange for an analysis of the newly rolled rolling stock 11 .

With the rolling mill described above, a previously unattainable flexibility in the rolling of rolling stock 11 can be achieved. In particular, each rolling mill can be activated individually 1-10 . It is also possible to set which fraction t3-t10 of its spring force-related suspension it compensates for each individual roll stand 1-10 . In addition, it can be specified for each individual stand whether or not it performs a monitor control, ie a correction of its desired roll gaps s3 ^* -s10 ^* based on the measured heights h and widths b of the measuring devices 15-19 .

As a result, each of the roll stands 1-10 can be operated as a sizing stand, a presing stand or as a removal stand. This is no longer a question of the structure of the respective roll stand 1-10 , but only a question of the corresponding setting of the roll gap controls, which can be carried out in seconds.

According to the exemplary embodiment, all roll stands 1-10 are designed identically. In particular, all mill stands 1-10 are adjustable via hydraulic cylinder units 12 . If it is known from the outset that only some of the roll stands 1-10 can be considered as sizing and presizing stands, the other roll stands, e.g. B. the mill stands 9 and 10 , but also employed in a different way who the. At least the presizing and sizing stands, i.e. at least the last four active roll stands 3-6 , should be hydraulically adjustable.

Reference list

1-10

Mill stands

11

Rolling stock

12th

Hydraulic cylinder unit

13

Roll gap control

14

parent computer

15-19

Measuring devices

20th

Tension measuring device

21

Storage device

22

Temperature measuring device

23

keyboard

24th

monitor
a3 adjustment path
b final height
C3 spring constant
F3-F10 rolling forces
F3 ^*

-F10 ^*

expected rolling forces
h final width
p3 working pressure
s3-s10 nips
s3 ^*

-s10 ^*

Target nip
t3-t10 fractions

Claims (17)

1. rolling mill for rolling rod-shaped rolling stock ( 11 ), for. B. steel bars or wire, with several adjustable on roll gaps (s3-s10), from the rolling stock ( 11 ) successively, to rolling stand pairs together milled active rolling stands ( 3-10 ), by means of which the rolling stock ( 11 ) with the application of rolling forces ( F3-F10) can be rolled to an end height (h) and a perpendicular end width (b), characterized in that

• - that the roll gaps (s3-s10) of the active roll stands ( 3-10 ) can be adjusted via hydraulic cylinder units ( 12 ),
• - That the hydraulic cylinder units ( 12 ) can be controlled by roll gap controls ( 13 ), by means of which spring force-related suspensions of the active roll stands ( 3-10 ) can be compensated for at least to a fraction (t3-t10), and
• - That the fractions (t3-t10) for each active roll stand ( 3-10 ) are separately adjustable.

2. Rolling mill according to claim 1, characterized in that in the rolling stands ( 3 , 4 ) (sizing stands) of the last pass through the pair of rolling stands, the spring force-related suspension of the rolling stock ( 11 ) later passed through the sizing stand ( 3 ) to a smaller fraction (t3) is the spring force-related spring-back of the sizing stand ( 4 ) that the roller has passed well ( 11 ). 3. Rolling mill according to claim 2, characterized in that the rolling stock ( 11 ) from the rolling stands ( 5 , 6 ) (presizing stands) at least one of the sizing stands ( 3 , 4 ) immediately upstream pair of stands is rolled such that the sizing stands ( 3 , 4 ) are operated in their most favorable dynamic range. 4. Rolling mill according to claim 3, characterized in that the spring force-related suspension of the rolling stock ( 11 ) later passed presizing stand ( 5 ) is compensated for to a smaller fraction (t5) than the rolling force-related suspension of the rolling stock ( 11 ) previously run through Presizing scaffold ( 6 ). 5. Rolling mill according to claim 3 or 4, characterized in that the spring force-related spring-ups of the sizing stands ( 3 , 4 ) are compensated on average to smaller fractions (t3, t4) than the spring-force-related spring-ups of the presizing stands ( 5 , 6 ). 6. Rolling mill according to claim 3, 4 or 5, characterized in that the roll gaps (s5, s6) of the presizing stands ( 5 , 6 ) from the roll gaps (s3, s4) of the sizing stands ( 3 , 4 ) are determined. 7. Rolling mill according to claim 3, 4, 5 or 6, characterized in that the presizing stands ( 5 , 6 ) is immediately upstream of at least one pair of rolling stands, in the rolling stands ( 7-10 ) (removal stands) the rolling stock ( 11 ) as strong as possible in cross section is reduced. 8. Rolling mill according to claim 7, characterized in that the spring force-related spring-ups of the removal stands ( 7-10 ) are at least substantially fully compensated. 9. Rolling mill according to one of claims 2 to 8, characterized in that the sizing stand ( 3 ) later passed through the rolling stock ( 11 ) has a measuring device ( 15 ) for detecting the end height (h) and end width (b) of the rolling stock ( 11 ) is subordinate and that the roll gaps (s3, s4) of the sizing stands ( 3 , 4 ) due to the detected final height (h) and final width (b) are correctable bar. 10. Rolling mill according to claim 9, characterized in that the other pairs of stands, preferably even each other Ren mill stand ( 4-10 ), measuring devices ( 17-19 ) for detecting the height and width of the rolling stock ( 11 ) are arranged. 11. Rolling mill according to one of the above claims, characterized in that it has at least one temperature measuring device ( 22 ) for measuring the temperature of the rolling stock ( 11 ). 12. Rolling mill according to one of the above claims, characterized, that the fractions (t3-t10) based on train and / or height and width measurements can be optimized during rolling. 13. Rolling mill according to one of the above claims, characterized in that it has a storage device ( 21 ) for storing a plurality of material properties of rolling stock ( 11 ), the final height (h), the final width (b), the stand parameters and the stand settings (s3 -s10, t3-t10), an input device ( 23 ) for entering the material properties, the end height (h) and the end width (b) of a new rolling stock ( 11 ) and a comparison device ( 14 ) for comparing the material properties Final height (h) and the final width (b) of the new rolling stock ( 11 ) with the material properties, the final height (h) and the final width (b) of the stored rolling stock ( 11 ) and the current Ge framework parameters with the saved framework parameters , so that the rolling stands ( 1-10 ) with matching stand parameters when rolling a new rolling stock ( 11 ) to the stand settings (s3-s10, t3 -t10) for an already rolled rolling mill t ( 11 ) can be preset with corresponding material properties and final dimensions (h, b). 14. rolling mill according to claim 13, characterized, that the stand parameters, the roll diameters and the stand settings gen (s3-s10, t3-t10), the roll gaps (s3-s10), the rolling speeds and which comprise fractions (t3-t10).   15. Rolling mill according to claim 13 or 14, characterized in that the material properties of the rolling stock ( 11 ) include the temperature, the initial dimensions and the quality of the rolling stock ( 11 ). 16. Rolling mill according to claim 13, 14 or 15, characterized in that in the storage device ( 21 ) also a plurality of rolling parameters (F3-F10) resulting during rolling of the rolling stock ( 11 ) can be stored and that the rolling mill is a comparison device ( 14 ) to compare the rolling parameters (F3-F10) resulting from the rolling of the new rolling stock ( 11 ) with the rolling parameters (F3-F10) corresponding to the new stand settings (s3-s10, t3-t10) and an output device ( 24 ) for outputting a warning signal in the event of significant deviations of the rolling parameters (F3 -F10) resulting from the rolling of the new rolling stock ( 11 ) from the rolling parameters (F3-F10) corresponding to the new stand settings (s3-s10, t3-t10). 17. rolling mill according to claim 16, characterized, that the rolling parameters (F3-F10) the rolling forces (F3-F10) and / or the Include rolling moments.